JP2019032101A - Heat source system control method and device of the same - Google Patents

Abstract

To provide a heat source system control method which can achieve simplification of control and attain sufficient energy saving effect, and to provide a device of the heat source system control method.SOLUTION: A heat source system control method for optimally controlling a heat source system 10 for sending cold water cooled by a heat source machine 12 to air conditioners 11a, 11b, 11c includes: a step where an upper limit value of a temperature of the cold water sent from the heat source machine 12 is calculated on the basis of load factors of the air conditioners 11a, 11b, 11c; a step where a setting value of the temperature of the cold water sent from the heat source machine 12 is calculated on the basis of the upper limit value of the calculated temperature of the sent cold water and the load factors of the heat source machine 12; and a step where operation control of the heat source machine 12 is performed on the basis of the calculated setting value of the temperature of the cold water.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a heat source system control method and apparatus for optimally controlling a heat source system that sends cold water cooled by a heat source unit to an air conditioner.

  In buildings such as office buildings, the proportion of energy consumption by heat source systems related to air conditioning equipment is increasing, and energy conservation measures are becoming increasingly important. Therefore, conventionally, in this type of building, a technique for optimally controlling the heat source system has been widely adopted.

  As a conventional technology of this type, for example, in Patent Document 1, measurement is made with reference to a cold / hot water set temperature specifying table in which the set temperature of the cold / hot water of the heat source device is associated with the load heat amount of the air conditioner A control device that specifies a set temperature corresponding to the load heat quantity of an air conditioner and controls the heat source unit so as to supply cold / hot water having the specified set temperature is described.

  Further, Patent Literature 2 is based on outside air state data and data representing the correlation between the outside air state suitable for operation of a representative air conditioner selected from a plurality of air conditioners that share heat source water and the water supply water supply temperature. Thus, a heat source control device that determines a target water supply temperature of the heat source water is described.

  Further, in Patent Document 3, the air temperature of the air conditioner and the cold water of the refrigerator are set so that the amount of energy consumption, the operating cost, or the amount of discharged carbon dioxide of the air conditioning equipment is minimized within the range satisfying the set air conditioning conditions. A control method for air conditioning equipment is described in which the set values of the temperature and the cooling water temperature of the cooling tower are changed and optimized.

  In addition, Patent Document 4 discloses a record of the amount of energy used by the heat source device, the amount of energy used by the cold / hot water pump, the temperature of the cold / hot water supplied from the heat source device, and the outside air temperature, which are collected periodically during operation of the heat source device. A water supply temperature control apparatus is described in which values are plotted in a multidimensional space, a response surface model is created by the RSM-S technique, and the current optimum water supply temperature is determined from the created response surface model.

JP2013-040705A JP 2017-003225 A JP 2004-053127 A JP 2010-236786 A

  However, in the technique described in Patent Document 1 described above, when a plurality of air conditioners are installed, the load factor of each air conditioner may vary greatly, and the chilled water supply temperature is set for an air conditioner with a low load factor. When calculated, there is a problem that an air conditioner with a high load factor cannot sufficiently perform heat treatment and cannot satisfy indoor environmental conditions.

  Further, the technique described in Patent Document 2 described above cannot sufficiently cope with the case where the optimum cold water supply temperature is different even if the outside air temperature humidity is the same. That is, for example, when the load factor of the air conditioner is large, the chilled water supply temperature cannot be set low, or when the load factor of the air conditioner is small, the chilled water supply temperature cannot be set high. There is a problem that it cannot be fully achieved.

  Further, the technique described in Patent Document 3 has a problem that the control system is complicated because there are many parameters and measurement points necessary for control, and a calculation speed is slow because of a large calculation load. .

  Further, in the technique described in Patent Document 4 described above, the section of the response surface model is cut out according to the outside air temperature to be measured, and the cold water supply temperature at which the energy consumption is minimized is calculated, which complicates the calculation model. Therefore, there is a problem that it cannot be easily incorporated into a control device of a general heat source system.

  The present invention has been made to solve the various problems described above, and aims to provide a heat source system control method and apparatus capable of simplifying control and obtaining a sufficient energy saving effect. It is.

  In order to achieve the above-described object, the present invention provides a heat source system control method for optimally controlling a heat source system that sends cold water cooled by a heat source unit to an air conditioner, based on a load factor of the air conditioner, Based on the calculated upper limit value of the chilled water temperature sent from the heat source machine, the calculated upper limit value of the chilled water feed temperature and the load factor of the heat source machine, the set value of the chilled water temperature sent from the heat source machine And a step of controlling the operation of the heat source unit based on the calculated set value of the cold water temperature.

  The heat source system control method according to the present invention calculates an upper limit value of the chilled water temperature using an approximate expression expressing a correlation between a load factor of the air conditioner and an upper limit value of the chilled water temperature delivered from the heat source device. And a step of calculating a set value of the chilled water temperature using an approximate expression expressing a correlation between a load factor of the heat source unit and a set value of the chilled water temperature sent from the heat source unit. It is preferable.

  Further, the present invention provides a heat source system control method for optimally controlling a heat source system that sends cold water cooled by a heat source device to an air conditioner, and is sent from the heat source device based on the measured outside air wet bulb temperature. Calculating the upper limit value of the chilled water temperature, calculating the set value of the chilled water temperature sent from the heat source unit based on the calculated upper limit value of the chilled water supply temperature and the load factor of the heat source unit; And a step of controlling the operation of the heat source unit based on the calculated set value of the cold water temperature.

  The heat source system control method according to the present invention uses an approximate expression that expresses a correlation between the measured outside wet bulb temperature and the upper limit value of the cold water temperature delivered from the heat source unit, and uses the approximate expression to express the upper limit value of the cold water temperature. Calculating the set value of the chilled water temperature using an approximate expression expressing the correlation between the load factor of the heat source unit and the set value of the chilled water temperature delivered from the heat source unit; Is preferably provided.

  Further, the present invention provides a heat source system control device for optimally controlling a heat source system that sends cold water cooled by a heat source unit to an air conditioner, and is sent from the heat source unit based on a load factor of the air conditioner. Means for calculating an upper limit value of the chilled water temperature, means for calculating a set value of the chilled water temperature sent from the heat source unit based on the calculated upper limit value of the chilled water supply temperature and the load factor of the heat source unit; Means for controlling the operation of the heat source unit based on the calculated set value of the cold water temperature.

  Further, the present invention provides a heat source system control device for optimally controlling a heat source system that sends cold water cooled by a heat source device to an air conditioner, and is sent from the heat source device based on the measured outside air wet bulb temperature. Means for calculating an upper limit value of the chilled water temperature, means for calculating a set value of the chilled water temperature sent from the heat source unit based on the calculated upper limit value of the chilled water supply temperature and the load factor of the heat source unit; And a means for controlling the operation of the heat source unit based on the set value of the calculated cold water temperature.

  According to the present invention, various excellent effects such as simplification of control of the heat source system and a sufficient energy saving effect can be obtained.

It is the schematic which shows the heat-source system in the 1st Embodiment of this invention. It is a flowchart which shows the method of calculating the upper limit of the cold-water temperature sent from a heat-source machine in the heat-source system control method which concerns on the 1st Embodiment of this invention. In the heat source system control method which concerns on the 1st Embodiment of this invention, it is a figure which shows the correlation with the load factor of an air conditioner, and the upper limit of the cold-water temperature sent from a heat source machine. It is a flowchart which shows the method of calculating the setting value of the cold water temperature sent from a heat-source machine in the heat-source system control method which concerns on the 1st Embodiment of this invention. In the heat source system control method which concerns on the 1st Embodiment of this invention, it is a figure which shows the correlation with the load factor of a heat source machine, and the setting value of the cold water temperature sent from a heat source machine. It is the schematic which shows the heat-source system in the 2nd Embodiment of this invention. It is a flowchart which shows the method of calculating the upper limit of the cold-water temperature sent from a heat-source machine in the heat-source system control method which concerns on the 2nd Embodiment of this invention. In the heat source system control method which concerns on the 2nd Embodiment of this invention, it is a figure which shows correlation with the upper limit of the cold water temperature sent out from an external air wet bulb temperature and a heat source machine.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the case where the present invention is applied to a water-cooled heat source system is described. However, this is merely an example, and the present invention can also be applied to an air-cooled heat source system.

  First, with reference to FIG. 1, the heat source system 10 in the 1st Embodiment of this invention is demonstrated.

  The heat source system 10 in the first embodiment includes a heat source unit 12 that cools cold water supplied to a plurality of air conditioners 11a, 11b, and 11c (three units are shown in FIG. 1) in a building, and a heat source. The cooling tower 13 which cools the cooling water supplied to the machine 12 and the calculating part 14 which controls the heat source machine 12 are provided, and the calculating part 14 comprises the control apparatus of the heat source control system 10. FIG.

  The heat source unit 12 is a water-cooled refrigerator, and a cold water pipe 15 is disposed between each air conditioner 11a, 11b, 11c and the heat source unit 12. The chilled water pipe 15 includes a chilled water main pipe 16 arranged around the heat source unit 12 and chilled water branch pipes 17a, 17b, 17c arranged in parallel around the air conditioners 11a, 11b, 11c, respectively. I have.

  In the chilled water main pipe 16, a chilled water pump 18 is disposed in the vicinity of the upstream side of the chilled water circulation direction (see the arrow in FIG. 1) with respect to the heat source device 12. The cold water main pipe 16 has a first cold water temperature sensor T1 disposed downstream of the heat source device 12 in the cold water circulation direction, and a second cold water temperature sensor T2 disposed between the heat source device 12 and the cold water pump 18. The first cold water temperature sensor T1 measures the cold water outlet temperature of the heat source unit 12, and the second cold water temperature sensor T2 measures the cold water inlet temperature of the heat source unit 12. Further, a first chilled water flow sensor F1 is disposed in the chilled water main pipe 16 on the upstream side in the chilled water circulation direction of the chilled water pump 18, and the first chilled water flow sensor F1 measures the flow of chilled water flowing through the chilled water main pipe 16. It is supposed to be. The measurement values of the first cold water temperature sensor T1, the second cold water temperature sensor T2, and the first cold water flow rate sensor F1 are transmitted to the calculation unit 14, respectively.

  The chilled water branch pipes 17a, 17b, and 17c are respectively provided with a third chilled water temperature sensor T3, a fourth chilled water temperature sensor T4, and a fifth chilled water on the upstream side and the downstream side in the chilled water circulation direction of the air conditioners 11a, 11b, and 11c, respectively. A temperature sensor T5, a sixth cold water temperature sensor T6, a seventh cold water temperature sensor T7, and an eighth cold water temperature sensor T8 are arranged. The third cold water temperature sensor T3, the fifth cold water temperature sensor T5, and the seventh cold water temperature sensor T7 measure the cold water inlet temperature of each of the air conditioners 11a, 11b, and 11c, and the fourth cold water temperature sensor T4 and the sixth cold water temperature sensor T4, respectively. The chilled water temperature sensor T6 and the eighth chilled water temperature sensor T8 measure the chilled water outlet temperatures of the air conditioners 11a, 11b, and 11c, respectively.

  The chilled water branch pipes 17a, 17b, and 17c include a second chilled water flow sensor F2 on the downstream side in the chilled water circulation direction of the fourth chilled water temperature sensor T4, the sixth chilled water temperature sensor T6, and the eighth chilled water temperature sensor T8, respectively. The 3rd cold water flow sensor F3 and the 4th cold water flow sensor F4 are arrange | positioned. The second chilled water flow rate sensor F2, the third chilled water flow rate sensor F3, and the fourth chilled water flow rate sensor F4 measure the flow rates of chilled water flowing through the chilled water branch pipes 17a, 17b, and 17c, respectively. The third cold water temperature sensor T3, the fourth cold water temperature sensor T4, the fifth cold water temperature sensor T5, the sixth cold water temperature sensor T6, the seventh cold water temperature sensor T7, the eighth cold water temperature sensor T8, and the second cold water flow rate sensor. The measured values of F2, the third chilled water flow sensor F3, and the fourth chilled water flow sensor F4 are transmitted to the calculation unit 14, respectively.

  A cooling water pipe 19 is disposed between the heat source unit 12 and the cooling tower 13. The cooling water pipe 19 is provided with a cooling water pump 20 in the vicinity of the upstream side in the cooling water circulation direction (see the arrow in FIG. 1) with respect to the heat source unit 12. In addition, a bypass pipe 21 is branched and provided in the cooling water pipe 19 so as to bypass the cooling tower 13, and a three-way electric valve 22 is provided at a junction of the bypass pipe 21 and the cooling water pipe 19. In addition, although measuring instruments, such as a cooling water flow sensor and a cooling water temperature sensor, are provided in the middle of the cooling water piping 19, those description and illustration are abbreviate | omitted.

  Next, a control method for the heat source system 10 according to the first embodiment of the present invention will be described with reference to FIGS. 2 to 5 in addition to FIG.

First, a method for calculating the upper limit value T _UL of the cold water temperature delivered from the heat source device 12 will be described.

As shown in step S10 of FIG. 2, the calculation unit 14 includes a third chilled water temperature sensor T3, a fourth chilled water temperature sensor T4, and a second chilled water temperature sensor T4, which are arranged around the air conditioners 11a, 11b, and 11c. Each of 5 chilled water temperature sensor T5, 6th chilled water temperature sensor T6, 7th chilled water temperature sensor T7, 8th chilled water temperature sensor T8, 2nd chilled water flow rate sensor F2, 3rd chilled water flow rate sensor F3, 4th chilled water flow rate sensor F4 from the measured values, each of the air conditioners 11a, 11b, on calculating the load process heat of 11c, by the following equation (1) calculates each of the air conditioners 11a, 11b, the load factor _{L ac} of 11c.

Air-conditioner load factor _Lac = Air-conditioner load processing heat amount ÷ Air-conditioner design processing heat amount (1)

  Next, in step S11, the calculation unit 14 calculates the upper limit value T of the chilled water temperature of each of the air conditioners 11a, 11b, and 11c using the following approximate expression (2).

T = aL _ac + b (2)

Here, the values of a and b in the approximate expression (2) are derived from the simulation using the heat source system 10 in the first embodiment as a model, and the load factor _Lac and the heat source of the air conditioners 11a, 11b, and 11c. It is obtained from FIG. 3 showing the correlation with the upper limit value of the cold water temperature delivered from the machine 12. In the approximate expression (2), a and b are different values for each air conditioner. In the case of FIG. 3, the upper limit value of the cold water supply temperature is set to 12 ° C., and the lower limit value is set to 7 ° C., and the coefficient a = −0.201 and the coefficient b = 27.3.

Next, in step S12, the calculation unit 14 determines that the upper limit value T of the chilled water temperature of each of the air conditioners 11a, 11b, and 11c calculated in step S11 is equal to or higher than the lower limit value _{TL of the} chilled water temperature at which the heat source unit 12 can operate. Judge whether each. And when it is judged that it is more than lower limit _{TL of} cold water temperature, it progresses to the following step S13.

In step S13, the calculation unit 14, each of the air conditioners 11a, 11b, the upper limit T of the chilled water temperature of 11c, or the determining each if more than the upper limit _{T H} of operable chilled water temperature of the heat source device 12. When it is determined to be equal to or less than the upper limit value T _H of the cold water temperature, the process proceeds to the next step S14.

In step S14, the calculation unit 14 sets the lowest value among the upper limit values T of the air conditioners 11a, 11b, and 11c calculated by the approximate expression (2) as the upper limit value T _UL of the cold water temperature.

On the other hand, when the calculation unit 14 determines in step S12 that the upper limit value T of the chilled water temperature of the air conditioners 11a, 11b, and 11c is not equal to or higher than the lower limit value _{TL of the} chilled water temperature at which the heat source unit 12 can operate, the process proceeds to step S15. Then, the lower limit value _TL of the cold water temperature at which the heat source device 12 can be operated is set to the upper limit value T _UL of the cold water temperature.

Further, in step S13, the calculation unit 14, the air conditioner 11a, 11b, the upper limit T of the chilled water temperature of 11c is determined to not less than the upper limit value _{T H} of the operable chilled water temperature of the heat source machine 12, in Step S16 proceeds to set the upper limit value _{T H} of the operable chilled water temperature of the heat source unit 12 the air conditioner 11a, 11b, the upper limit _{T UL} chilled water temperature of 11c.

Next, a method for calculating the set value T _SP of the cold water temperature delivered from the heat source device 12 will be described.

As shown in step S20 of FIG. 4, the calculation unit 14 includes a first chilled water temperature sensor T1, a second chilled water temperature sensor T2, and a first chilled water flow rate sensor disposed around the heat source unit 12. After calculating the load processing heat quantity of the heat source machine 12 from each measured value of F1, the load factor _Lhe of the heat source machine 12 is calculated by the following equation (3).

Heat source unit load factor L _he = heat source unit load processing heat amount ÷ heat source unit design processing heat amount (3)

Next, in step S <b> 21, the calculation unit 14 calculates a calculation value T ₀ of the chilled water temperature of the heat source machine 12 that minimizes the energy consumption by the following approximate expression (4).

T ₀ = eL _he + f (4)

Here, the values of e and f of the approximate expression (4) are derived from the simulation using the heat source system 10 as a model, and are sent from the heat source unit 12 and the load factor _Lhe of the heat source unit 12 with the minimum energy consumption. FIG. 5 shows the correlation with the optimum value of the chilled water temperature. In this case, the upper limit value of the cold water supply temperature is set to 12 ° C., the lower limit value is set to 7 ° C., and the coefficient e = −0.0867 and the coefficient f = 15.6.

Then, in step S22, the calculation unit 14, determining whether the calculated value T ₀ of chilled water temperature of the heat source unit 12 calculated in step S21 is, the lower limit of the operable chilled water temperature of the heat source apparatus 12 T _L or more To do. And when it is judged that it is more than lower limit _{TL of} cold water temperature, it progresses to the following step S23.

In step S23, the calculation unit 14, the arithmetic value _{T 0} of chilled water temperature of the heat source machine 12, the air conditioner 11a, 11b, to determine whether the upper limit of the set value _{T UL} following the cold water temperature of 11c. And when it is judged that it is below the upper limit set value _TUL of cold water temperature, it progresses to the following step S24.

In step S24, the arithmetic unit 14 sets the calculated value T ₀ of chilled water temperature of the heat source unit 12 which is calculated in the above approximate expression (4) to a set value T _SP chilled water temperature.

On the other hand, in step S22, the calculation unit 14, the operation value T ₀ of chilled water temperature of the heat source apparatus 12 is determined to not more than the lower limit T _L of operable chilled water temperature of the heat source unit 12, the process proceeds to step S25, the heat source The lower limit value _TL of the cold water temperature at which the machine 12 can be operated is set to the set value T _SP of the cold water temperature.

Further, in step S23, the calculation unit 14, the arithmetic value _{T 0} of chilled water temperature of the heat source machine 12, the air conditioner 11a, 11b, if it is determined that not less than the upper limit set value _{T UL} chilled water temperature of 11c, Step S26 the process proceeds, the air conditioner 11a, 11b, setting the upper limit of the set value _{T UL} chilled water temperature of 11c to the set value _{T SP} chilled water temperature.

Then, the arithmetic unit 14, based on the set value T _SP of the thus chilled water temperature calculated by, to optimally control the heat source apparatus 12.

  Next, with reference to FIG. 6, the heat source system 30 in the 2nd Embodiment of this invention is demonstrated. In the following description, components equivalent to those of the heat source system 10 in the first embodiment described above are denoted by the same reference numerals as those in FIG. 1 and detailed description thereof is omitted.

  The heat source system 30 in the second embodiment includes a plurality of air conditioners 11a, 11b, 11c (three are shown in FIG. 6), a heat source, as in the heat source system 10 in the first embodiment described above. Machine 12, cooling tower 13, operation unit 14, chilled water pipe 15, chilled water branch pipes 17a, 17b, 17c, chilled water pump 18, first chilled water temperature sensor T1, second chilled water temperature sensor T2, first chilled water flow rate sensor F1, cooling A water pipe 19, a cooling water pump 20, a bypass pipe 21, and a three-way motor operated valve 22 are provided.

  However, unlike the heat source system 10 in the first embodiment described above, the heat source system 30 in the second embodiment has a third cold water temperature sensor T3, a third chilled water temperature sensor T3, and the like around each air conditioner 11a, 11b, 11c. 4 cold water temperature sensor T4, 5th cold water temperature sensor T5, 6th cold water temperature sensor T6, 7th cold water temperature sensor T7, 8th cold water temperature sensor T8, 2nd cold water flow sensor F2, 3rd cold water flow sensor F3, 4 The cold water flow sensor F4 is not provided. Instead, the heat source system 30 in the second embodiment is provided with an outside air sensor W1 that measures the outside air wet bulb temperature outside the building, and the measurement value obtained by the outside air sensor W1 is transmitted to the calculation unit 14. It has become so.

  Next, a method for controlling the heat source system 30 according to the second embodiment of the present invention will be described with reference to FIGS. 7 and 8 in addition to FIG.

First, a method for calculating the upper limit value T _UL of the cold water temperature delivered from the heat source device 12 will be described.

  As shown in step S30 of FIG. 7, the calculation unit 14 determines the air conditioners 11a, 11b, and 11c from the value of the outside air wet bulb temperature measured by the outside air sensor W1, as shown in step S31. The upper limit value T of the chilled water temperature is calculated by the following approximate expression (5).

T = cO _WB + d (5)

  Here, the values of c and d in the approximate expression (5) are derived from the simulation using the heat source system 30 in the second embodiment as a model, and the temperature of the outside wet bulb and the temperature of the chilled water sent from the heat source unit 12. 8 showing the correlation with the upper limit value. C and d in the approximate expression (5) are different values for each air conditioner. In the case of FIG. 8, the upper limit value of the cold water supply temperature is set to 12 ° C., the lower limit value is set to 7 ° C., and the coefficient c = −0.322 and the coefficient d = 16.4.

Next, in step S32, the calculation unit 14 determines that the upper limit value T of the chilled water temperature of each of the air conditioners 11a, 11b, and 11c calculated in step S31 is equal to or higher than the lower limit value _{TL of the} chilled water temperature at which the heat source unit 12 can operate. Determine whether or not. And when it is judged that it is more than lower limit _{TL of} cold water temperature, it progresses to the following step S33.

In step S33, the calculation unit 14, each of the air conditioners 11a, 11b, the upper limit T of the chilled water temperature of 11c, or the determining each if more than the upper limit _{T H} of operable chilled water temperature of the heat source device 12. When it is determined to be equal to or less than the upper limit value T _H of the cold water temperature, the process proceeds to the next step S34.

In step S34, the calculation unit 14 sets the lowest value among the upper limit values T of the air conditioners 11a, 11b, and 11c calculated by the approximate expression (5) as the upper limit value T _UL of the cold water temperature.

On the other hand, when the calculation unit 14 determines in step S32 that the upper limit calculation value T of the chilled water temperature of the air conditioners 11a, 11b, and 11c is not equal to or greater than the lower limit value _{TL of the} chilled water temperature at which the heat source unit 12 can operate. Proceeding to S35, the lower limit value _TL of the cold water temperature at which the heat source device 12 can be operated is set to the upper limit value T _UL of the cold water temperature.

Further, in step S33, the calculation unit 14, the air conditioner 11a, 11b, the upper limit T of the chilled water temperature of 11c is determined to not less than the upper limit value _{T H} of the operable chilled water temperature of the heat source machine 12, in step S36 proceeds to set the upper limit value _{T H} of the operable chilled water temperature of the heat source unit 12 the air conditioner 11a, 11b, the upper limit _{T UL} chilled water temperature of 11c.

Next, based on the upper limit value of the cold water supply temperature calculated as described above and the load factor of the heat source unit 12, the set value T _SP of the cold water temperature delivered from the heat source unit 12 is calculated. Since it is the same as the case of the heat source system 10 in the first embodiment described above (see FIGS. 4 and 5), the description and illustration thereof are omitted.

When the set value T _SP chilled water temperature sent from the heat source unit 12 is calculated, the calculation unit 14, based on the set value T _SP chilled water temperature, to optimally control the heat source apparatus 12.

  As described above, according to the control method and apparatus for the heat source systems 10 and 30 according to the first and second embodiments of the present invention, it is a case where air conditioners having greatly different heat loads exist in the building. However, the energy-saving operation control of the heat source unit 12 can be optimally performed while satisfying the indoor environment conditions. Further, by calculating the upper limit value or the optimum set value of the cold water supply temperature by the approximate expression, the calculation load is reduced and the calculation model is simplified, so that it can be easily introduced into a general heat source system. it can.

  Furthermore, according to the control method and apparatus of the heat source system 30 according to the second embodiment of the present invention, the cold water supply temperature upper limit value of the air conditioner is calculated from the outdoor wet bulb temperature, the cold water inlet / outlet temperature difference of the heat source unit 12 and the flow rate. In addition, the set value of the cold water supply temperature of the heat source device can be calculated, and the energy-saving operation control can be optimally performed while suppressing the number of measurement devices installed and the number of measurement values to a minimum.

  In the embodiment of the present invention described above, the approximate expressions (2), (4), and (5) are all expressed by linear expressions, but this is not intended to limit the approximate expressions to linear expressions. Absent. That is, these approximate expressions (2), (4), and (5) may be expressions other than the primary expression such as a quadratic expression, a cubic expression, and a polynomial expression as long as they are expressed by one expression. Moreover, you may use the table which shows each correlation instead of these approximate expressions.

  Moreover, since the above-mentioned description of embodiment of this invention has demonstrated the preferred embodiment in the heat-source system control method which concerns on this invention, and its apparatus, various technically preferable restrictions are attached | subjected. In some cases, the technical scope of the present invention is not limited to these embodiments unless specifically described to limit the present invention. That is, the above-described components in the embodiment of the present invention can be appropriately replaced with existing components and the like, and various variations including combinations with other existing components are possible. The description of the embodiment of the present invention described above does not limit the contents of the invention described in the claims.

DESCRIPTION OF SYMBOLS 10 Heat source system 11a, 11b, 11c Air conditioner 12 Heat source machine 14 Calculation part (heat source system control apparatus)
30 Heat source system

Claims (6)

In a heat source system control method for optimally controlling a heat source system that sends cold water cooled by a heat source machine to an air conditioner,
Based on the load factor of the air conditioner, calculating the upper limit value of the cold water temperature sent from the heat source machine,
Calculating a set value of the cold water temperature delivered from the heat source unit based on the calculated upper limit value of the cold water supply temperature and the load factor of the heat source unit;
A step of controlling the operation of the heat source unit based on the set value of the calculated cold water temperature;
A heat source system control method comprising: Calculating an upper limit value of the cold water temperature using an approximate expression expressing a correlation between a load factor of the air conditioner and an upper limit value of the cold water temperature delivered from the heat source device;
A step of calculating a set value of the cold water temperature using an approximate expression expressing a correlation between a load factor of the heat source machine and a set value of the cold water temperature delivered from the heat source machine;
The heat source system control method according to claim 1, comprising: In a heat source system control method for optimally controlling a heat source system that sends cold water cooled by a heat source machine to an air conditioner,
A step of calculating an upper limit value of the cold water temperature delivered from the heat source unit based on the measured outside air wet bulb temperature;
Calculating a set value of the cold water temperature delivered from the heat source unit based on the calculated upper limit value of the cold water supply temperature and the load factor of the heat source unit;
A step of controlling the operation of the heat source unit based on the set value of the calculated cold water temperature;
A heat source system control method comprising: Calculating an upper limit value of the cold water temperature using an approximate expression expressing a correlation between the measured outside wet bulb temperature and the upper limit value of the cold water temperature sent from the heat source unit;
A step of calculating a set value of the cold water temperature using an approximate expression expressing a correlation between a load factor of the heat source machine and a set value of the cold water temperature delivered from the heat source machine;
The heat source system control method according to claim 3, further comprising: In a heat source system controller for optimally controlling a heat source system that sends cold water cooled by a heat source device to an air conditioner,
Based on the load factor of the air conditioner, means for calculating the upper limit value of the cold water temperature sent from the heat source unit;
Means for calculating a set value of the cold water temperature delivered from the heat source unit based on the calculated upper limit value of the cold water supply temperature and the load factor of the heat source unit;
Means for controlling the operation of the heat source unit based on the set value of the calculated cold water temperature;
A heat source system control device comprising: In a heat source system controller for optimally controlling a heat source system that sends cold water cooled by a heat source device to an air conditioner,
Means for calculating the upper limit value of the cold water temperature sent from the heat source unit based on the measured outside air wet bulb temperature;
Means for calculating a set value of the cold water temperature delivered from the heat source unit based on the calculated upper limit value of the cold water supply temperature and the load factor of the heat source unit;
Means for controlling the operation of the heat source unit based on the set value of the calculated cold water temperature;
A heat source system control device comprising:

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